design calculation of pressure vessel

File tính mẫu cho 1 bồn chứa áp lực theo tiêu chuẩn ASME Code Section VIII Division 1. Tài liệu mô tả tương đối cụ thể về cách tính toán, trích dẫn các công thức trong tiêu chuẩn ASME.tên thiết bị: Gas Filterđường kính trong ID = 1250mm

Trang 1

CademPVDby CADEM Softwares

Most value for money software for the mechanical design of process equipment

Trial version available on our website www.cadem.in

• 28 years of equipment design experience captured, polished, compacted and is now ready for transfer todesigners, fabricators and plant engineers

• Intelligent, works with minimum inputs

For instance, in case of say a body flange, the software automatically evaluates optimum configuration ofall undefined parameters: Flange OD, Flange ID, PCD, Number and Size of bolts, Gasket OD & ID, etc.meeting the requirements of the specified equipment design code

• Generates final design at estimation stage, saves more than 80% of your design & estimation time

• Earn more as you save on costing and quotation making time

• High quality documentation with all formulae and relevant code clauses

• Most importantly, the user need not be a hard core designer

Address: Office No 19, SC-1 Building,

Kohinoor Estate, Wakdewadi, Pune-Mumbai Road, Pune 411003, Maharashtra, India

@facebook: www.facebook.com/cademindia OR www.cadem.in/facebook

@youtube: www.youtube.com/cademchannel OR www.cadem.in/youtube

@linkedin: www.linkedin.com/company/cadem OR www.cadem.in/linkedin

@google+: http://plus.google.com/116314947079178385899 OR www.cadem.in/googleplus

@twitter: www.twitter.com/cademindia OR www.cadem.in/twitter

YOU CAN DOWNLOAD THIS DOCUMENT AND OTHERS AT www.cadem.in/links

IS 6533

Trang 2

EXAMPLE NO PV-01

DESIGN

OF PRESSURE VESSEL (GAS FILTER)

NOTE:

1) Link to youtube video of this design:

http://www.youtube.com/watch?v=3Y0yrt1Z6fI&list=PLPL8SPZUxm-mFqQZceyhr13QYDEruelJx

2) As you can see in the video, the inbuilt intelligence in the software generates all

information by itself Eg: For a body flange, the software evaluates all the undefined parameters Flange OD, Flange ID, PCD, Number and Size of bolts, Gasket OD & ID, etc meeting the requirements of specified equipment design code

3) In case of any changes to the interconnected shell geometry and / or design conditions (pressure / temperature) including material of constructions, these dimensions

automatically regenerated by the software to meet the new requirements

4) The software can generate cost estimation and BOM in Excel.

This example covers design of a simple pressure vessel This pressure vessel has a top flat cover and a bottom dished end The top cover is of bolted type and is connected to the shell through top body flange The pressure vessel is provided with lugs support and lifting lug.

Trang 3

'CademPVD' Version 14.91 by CADEM Softwares , Pune , Website www.cadem.in

Index

Designed By / Revision and Date / R00 , 30-03-2015 23:35:19

1 Title page & equipment info

2 Design data

3 Material of constructions

4 Effective Pressures

5 Weight summary report

6 Test pressure calculations (shell side)

7 Wind load calculations

8 Seismic load calculations

9 Design of Cover (Front)

10 Design of Cover (Front)

11 Design of Shell Flng (Front)

12 Design of Shell Flng (Front)

13 Design of Main Shell

14 Design of Dished End (Rear)

15 Design of Lug Support

16 Design of Lug Support

25 Design of Lifting Lugs

26 Foundation load data

27 C.G Data

Trang 4

EQUIPMENT INFORMATION :

DESIGN & REVIEWAL :

INSPECTION & APPROVAL :

EQUIPMENT DATA :

OTHER DATA :

Length, Shell (W.L to W.L) / Overall 1650 / 2254.6 mm

Empty weight + external weights 1898.3 kgf

Trang 5

(1) PROCESS DETAILS :

(3) TEST PR : kgf/mm² g

(4) TEMPERATURE : °C

(5) ALLOWANCES : mm

(6) RADIOGRAPHY & JOINT EFFICIENCY :

VESSEL DESIGN DATA

kg/m³

Operating Process Gas 10

RADIOGRAPHY JOINT EFFICIENCY

Shell Spot + T Joints 0.85

Trang 6

VESSEL DESIGN DATA

1 MATERIAL OF CONSTRUCTION :

2 NOZZLE CONNECTIONS :

3 INSULATION & CLADDING:

Shell side

Shell SA-516 GR 70 Plt [UNS:K02700]

Head SA-516 GR 70 Plt [UNS:K02700]

Body flange SA-105 Frg [UNS:K03504]

Body flange cover SA-516 GR 70 Plt [UNS:K02700]

Liner

Shell side

Nozzle neck <= NPS 40 SA-106 GR B Smls Pipe[UNS:K03006]

Flange SA-105 Frg [UNS:K03504]

Cover flange SA-105 Frg [UNS:K03504]

Nozzle NPS > 40 & < 200 SA-106 GR B Smls Pipe [UNS:K03006]

Flange SA-105 Frg [UNS:K03504]

Cover flange SA-105 Frg [UNS:K03504]

Nozzle neck >= NPS 200 SA-516 GR 70 Plt [UNS:K02700]

Flange SA-516 GR 70 Plt [UNS:K02700]

Cover flange SA-516 GR 70 Plt [UNS:K02700]

Pad flange SA-516 GR 70 Plt [UNS:K02700]

Pad flange cover SA-516 GR 70 Plt [UNS:K02700]

Manhole flange SA-516 GR 70 Plt [UNS:K02700]

Manhole cover SA-516 GR 70 Plt [UNS:K02700]

Reinforcement pad SA-516 GR 70 Plt [UNS:K02700]

External bolt SA-193 GR B7 Bolt [UNS:G41400]

External gasket Spiral metal wound CAF filled (S.S.)

Stiffener SA-516 GR 70 Plt [UNS:K02700]

Lifting lug IS-2062 GR A Plt

Support IS-2062 GR A Plt

Anchor bolt Commercial CS Bolt

Mat / Density / Thk Rockwool (Mineral Fibre) / 136.2 kg/m³ / 25 mm

Mat / Thk Al sheet / 1.191 mm

Trang 7

SUMMARY OF EFFECTIVE DESIGN PRESSURES IN kgf/mm² g VS TEMPERATURE IN °C

Sr Item name Temp Inside pr Liquid pr Effective pr.

Trang 8

ITEM WISE WEIGHT SUMMARY

Sr.No Item name Item size Empty wt Volume Filled wt

3 Gasket Flng (Front) 1313.5 OD x 1250 ID, 4.763 Thk 0.1 0 0.1

4 Bolt Flng (Front) Hex Head Bolt M24 x 243.128 Lg, 56 Nos. 48.76 0 48.76

7 Gusset Plate 200 Long x 190 Wide x 16 Thk, 8 Nos. 38.51 0 38.51

8 Anchor Bolt Anchor M20 x 200 Lg, 4 Nos 1.99 0 1.99

9 Support Pad 270 Long x 292 Wide x 10 Thk, 4 Nos. 24.97 0 24.97

10 N 01 ANSIB36.10, 150 NPS Sch.80, 156 Lg 6.697 0.00262 6.728

11 Flange [N 01] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08

12 Gasket [N 01] 166.329 OD x 146.329 ID, 4.763 Thk 0.1 0 0.1

13 Bolt [N 01] Hex Head Bolt M20 x 86.125 Lg, 8 Nos. 1.714 0 1.714

14 Counter Flng [N 01] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08

15 Reinf [N 01] 292.659 OD x 171.275 ID x 10Thk 3.501 0 3.501

16 N 02 ANSIB36.10, 150 NPS Sch.80, 156 Lg 6.697 0.00262 6.728

18 Gasket [N 02] 166.329 OD x 146.329 ID, 4.763 Thk 0.1 0 0.1

20 Counter Flng [N 02] Weld Neck, ANSI B16.5, RF, 150# for 150 NPS Sch 80 Pipe 8.08 0 8.08

21 Reinf [N 02] 292.659 OD x 171.275 ID x 10Thk 3.501 0 3.501

22 N 03 ANSIB36.10, 50 NPS Sch.160, 150 Lg 1.682 0.00022 1.684

24 Gasket [N 03] 62.85 OD x 42.85 ID, 4.763Thk 0.1 0 0.1

26 Bolted Cover [N 03] Weld Neck, ANSI B16.5, RF, 150# for 50 160 NPS Pipe 2.522 0 2.522

120 Long x 70 Wide x 12 Thk,

Trang 9

27 Lifting Lugs 2 Nos. 1.596 0 1.596

28 Pad (Lifting Lugs) 70 Long x 170 Wide x 8 Thk, 2Nos. 1.507 0 1.507

29 Insulation 4084.07 W x 3754.584 L, 25 Thk 52.2 0 52.2

30 Cladding 4087.811 W x 3754.584 L, 1.191 Thk 5.058 0 5.05831

Trang 10

TEST PRESSURES CALCULATION AS PER UG-99 / UG-100 : Vessel Inside

Legend :

Test Pressure Calculations

Pressure due to hydro liquid column, [ Plh ]

Sr.

No Item Name

Pressure ( kgf/mm² g ) Stress Correction ( kgf/mm² )

Pi = Internal positive pressure

Pl = Pressure due to design liquid column

Pe = Internal vacuum pressure

Pc = External negative pressure

Peff = Pi + Pl + Pc

Sfo = Allowabe stress at design temperature

Sfa = Allowable stress at ambient temperature

Pt = MAX [ Peff + Pc, Pe ] x ( Sfa / Sfo )

Trang 11

Vessel Inside

Legend :

CALC OF MIN DESIGN METAL TEMPERATURE Design Mode 1 , Corroded Condition

Sdt = Pressure due to design liquid column

tn = Stress at design metal temperature

tg = Nominal item thickness excluding corrosion and thinning

tr = Governing metal thickness for the item

Tg = Required minimum thickness of the item

Tm = Minimum metal temperature for the the item

Tc = MDMT Correction

MDMT = Final MDMT for the item = Tm - Tc

Trang 12

EXTREME FIBRE ELONGATION CALCULATION

Legend :

1 Main Shell SA-516 GR 70 Plt [UNS:K02700] 625 10 1 0.8 False

2 Dished End (Rear) SA-516 GR 70 Plt [UNS:K02700] 1130 10 2 0.664 False3

Trang 13

1 DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition ) :

3 CALCULATION OF FORCES AND MOMENTS:

WIND LOAD CALCULATION

Basic wind speed ( Section 5.2 ) Vb 50 m/s

Expected life of equipment ( Section 5.3.1 ) 25 Years

Probability factor (Risk coeff) ( Section 5.3.1 ) K1 0.902

Terrain category ( Section 5.3.2 ) Category 2

Structure class ( Section 5.3.2.2 ) Class B

Topography factor ( Section 5.3.3 ) K3 1.3

Force coefficient (Shape factor) Cf 0.8

Size and height factor ( Section 5.3.2 ) K2 0.98

Effective transverse cross sectional area

Trang 14

2 CALCULATION OF FORCES AND MOMENTS:

SEISMIC LOAD CALCULATION

Importance factor ( Table-6 , 2002 ) I 1.5

Seismic zone factor ( Table-2 , 2002 ) Z 0.16

Response reduction factor ( Table-7 , 2002 ) R 2.9

Spectral accelerations coeff ( Fig 2 , 2002 ) Sa / g 2.5, Use max value

Damping correction factor ( Table-3 , 2002 ) Cf 1

Seismic coefficient ( Clause-6.4.2 , 2002 )

Trang 15

2 COVER DATA :

3 BOLTING DATA :

4 LINER DATA :

5 GASKET DATA :

6 BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1) :

Total joint - contact surface compression load [Hp]

DESIGN OF FLAT BOLTED HEAD ( INTERNAL ) Cover (Front)

Code allw stress @ design temp Sfo 14.06 kgf/mm²

Code allw stress @ atm temp Sfa 14.06 kgf/mm²

Code allw stress @ design temp Sb 17.58 kgf/mm²

Code allw stress @ atm temp Sa 17.58 kgf/mm²

Width of gasket ( as per Table 2-5.2 ) 31.75 mm

Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm

Effective gasket width ( as per Table 2-5.2 ) b 9.554 mm

Dia at load reaction ( see Table 2-5.2 ) G 1294.4 mm

Effective pass partition gasket width b' 0 mm

Trang 16

= 27973 + 157907.4

= 185880.4 kgf

Minimum required bolt load for gasket seating [Wm2]

= (  x b x G + b' x Lp ) x y

= (  x 9.554 x 1294.4 + 0 x 0 ) x 7.031

= 273152.4 kgf

8 BOLT AREAS AS PER APPENDIX 2-5 (d) :

Total required cross-sectional area of bolts [Am]

= MAX [ Wm2 / Sa , Wm1 / Sb ] For Internal '+' Pr Design

= Wm2 / Sa For External Pr & Self Sealing Design

= 15540.6 mm²

Actual bolt area using root diameter [Ab]

= 17513.9 mm²

Flange design bolt load for the gasket seating [W]

= 0.5 x ( Am + Ab ) x Sa x 1 average bolt area

= Ab x Sa x 1 full bolt area

= 307837.2 kgf ( Full bolt area and margin factor of 1 )

9 CHECK FOR GASKET CRUSHING :

Minimum gasket width required [Nmin]

= Ab x Sb / ( 2 x  x y x G )

= 17513.9 x 17.58 / ( 2 x x 7.031 x 1294.4 )

= 5.384 mm

10 DESIGN CALCULATION AS PER UG 34, BOLTING CONDITION :

Required thickness for bolting condition [t]

= G x SQRT [ 1.9 x W x 0.5 x ( PCD - G ) / ( Sfa x E x G 3 ) ]

= 1294.4 x SQRT [ 1.9 x 307837.2 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) ]

= 33.2 mm

11 DESIGN CALCULATION AS PER UG 34, OPERATING CONDITION :

Required thickness for operating condition [t]

= G x SQRT { [ C x P / ( Sfo x E ) ] + 1.9 x Wm1 x 0.5 x ( PCD - G ) / ( Sfo x E x G 3 ) }

= 1294.4 x SQRT { [ 0.3 x 0.12 / ( 14.06 x 1 ) ] + 1.9 x 185880.4 x 0.5 x ( 1363 - 1294.4 ) /

( 14.06 x 1 x 1294.4 3 ) }

= 70.65 mm

Factor C taken from fig UG 34 or user input 0.3

C = Min ( 2 x 0.3, 0.75 ) for self reinf

C = 0.3 in other cases

Trang 17

2 COVER DATA :

4 LINER DATA :

5 GASKET DATA :

DESIGN OF FLAT BOLTED HEAD ( EXTERNAL ) Cover (Front)

Width of gasket ( as per Table 2-5.2 ) 31.75 mm

Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm

Trang 18

= 2458.4 + 13877.8

= 16336.3 kgf

= ( p x b x G + b' x Lp ) x y

= ( p x 9.554 x 1294.4 + 0 x 0 ) x 7.031

= 273152.4 kgf

8 BOLT AREAS AS PER APPENDIX 2-5 (d) :

= 15540.6 mm²

= 17513.9 mm²

9 CHECK FOR GASKET CRUSHING :

= Ab x Sb / ( 2 x p x y x G )

= 17513.9 x 17.58 / ( 2 xp x 7.031 x 1294.4 )

= 5.384 mm

10 DESIGN CALCULATION AS PER UG 34, BOLTING CONDITION :

Required thickness for bolting condition [t]

= G x SQRT [ 1.9 x W x 0.5 x ( PCD - G ) / ( Sfa x E x G 3 ) ]

= 1294.4 x SQRT [ 1.9 x 307837.2 x 0.5 x ( 1363 - 1294.4 ) / ( 14.06 x 1 x 1294.4 3 ) ]

= 33.2 mm

11 DESIGN CALCULATION AS PER UG 34, OPERATING CONDITION :

Required thickness for operating condition [t]

= G x SQRT { [ C x P / ( Sfo x E ) ] + 1.9 x Wm1 x 0.5 x ( PCD - G ) / ( Sfo x E x G 3 ) }

= 1294.4 x SQRT { [ 0.3 x 0.01055 / ( 14.06 x 1 ) ] + 1.9 x 16336.3 x 0.5 x ( 1363 - 1294.4 ) /

( 14.06 x 1 x 1294.4 3 ) }

= 32.29 mm

Factor C taken from fig UG 34 or user input 0.3

C = Min ( 2 x 0.3, 0.75 ) for self reinf

C = 0.3 in other cases

Trang 19

2 FLANGE DATA :

4 LINER DATA :

5 GASKET DATA :

5a Flange gasket data :

5b Partition groove gasket data (For H.E body flange) :

Flange gakset surface finish Serrated (Normal)

Counter gakset surface finish Serrated (Normal)

Applicalbe gasket sketch in Table 2-5.2 Type 1B

Applicable gasket column in Table 2-5.2 1

Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y 7.031 kgf/mm²

Gasket factor ( from Table 2-5.1 ) m 3

Width of gasket ( as per Table 2-5.2 ) N 28.75 mm

Width of gasket ( as per Table 2-5.2 ) w 28.75 mm

Width of raised face or gasket contact width 31.75 mm

( as per Table 2-5.2 )Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm

Trang 20

6 BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)

Minimum required bolt load for operating condition [Wm1b]

( from mating flange )

7 BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2)

= (p x b x G x y + b' x Lp x y' )

= ( p x 9.554 x 1294.4 x 7.031 + 0 x 0 x 0 )

= 273152.4 kgf

8 BOLT AREAS AS PER APPENDIX 2-5 (d)

= 15540.6 mm²

= 17513.9 mm²

9 CHECK FOR GASKET CRUSHING

= Ab x Sb / ( 2 x p x y x G )

= 17513.9 x 17.58 / ( 2 xp x 7.031 x 1294.4 )

= 5.384 mm

10 BOLT SPACING CORRECTION FACTOR

As per Brownell & Young or IS 2825,

= SQRT [ Bolt spacing / ( 2 x db + t ) ]

As per TEMA or BS 5500,

= SQRT [ Bolt spacing / Bmax ] where,

Bmax = maximum recommended bolt spacing = 2 x db + 6 x t / ( m + 0.5 )Brownell & Young, Cf = 1 ( min equal to 1 )

11 LOADS AND FORCES DURING OPERATING CONDITION AS PER APPENDIX 2-3

Hydrostatic end force on area inside of flange [HD]

12 MOMENT ARMS FOR FLANGE LOADS AS PER TABLE 2-6

Radial distance from the bolt circle to intersection of hub and back of flange, as per Appendix 2-3 [R]

= 0.5 x ( C - B ) - g1

= 0.5 x ( 1363 - 1256 ) - 17

Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y' 0 kgf/mm²Gasket factor ( from Table 2-5.1 ) m' 0

Trang 21

13 FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6

Component of moment due to HD [MD]

14 LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3

Gasket load for seating condition [HG]

= W

= 307837.2 kgf

15 MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6

Total moment acting on the flange for gasket seating [MO']

Trang 22

18 FLANGE STRESSES AS PER APPENDIX 2-7 & 2-8

Equivalent moment [Mmax]

= MAX [ MO , MO' x Sfo / Sfa ]

Trang 23

2 FLANGE DATA :

4 LINER DATA :

5 GASKET DATA :

5a Flange gasket data :

5b Partition groove gasket data (For H.E body flange) :

Flange gakset surface finish Serrated (Normal)

Counter gakset surface finish Serrated (Normal)

Applicalbe gasket sketch in Table 2-5.2 Type 1B

Applicable gasket column in Table 2-5.2 1

Gasket seating stress ( refer to Note 1, Table 2-5.1 ) y 7.031 kgf/mm²

Gasket factor ( from Table 2-5.1 ) m 3

Width of gasket ( as per Table 2-5.2 ) N 28.75 mm

Width of gasket ( as per Table 2-5.2 ) w 28.75 mm

Width of raised face or gasket contact width 31.75 mm

( as per Table 2-5.2 )Basic gasket seating width ( as per Table 2-5.2 ) b0 14.38 mm

Trang 24

6 BOLT LOAD CALCULATIONS AS PER APPENDIX 2-5 (b1)

Minimum required bolt load for operating condition [Wm1b]

( from mating flange )

7 BOLT LOAD CALCULATION AS PER APPENDIX 2-5 (b2)

= (p x b x G x y + b' x Lp x y' )

= ( p x 9.554 x 1294.4 x 7.031 + 0 x 0 x 0 )

= 273152.4 kgf

8 BOLT AREAS AS PER APPENDIX 2-5 (d)

= 15540.6 mm²

= 17513.9 mm²

9 CHECK FOR GASKET CRUSHING

= Ab x Sb / ( 2 x p x y x G )

= 17513.9 x 17.58 / ( 2 xp x 7.031 x 1294.4 )

= 5.384 mm

10 BOLT SPACING CORRECTION FACTOR

As per Brownell & Young or IS 2825,

= SQRT [ Bolt spacing / ( 2 x db + t ) ]

As per TEMA or BS 5500,

= SQRT [ Bolt spacing / Bmax ] where,

Bmax = maximum recommended bolt spacing = 2 x db + 6 x t / ( m + 0.5 )Brownell & Young, Cf = 1 ( min equal to 1 )

11 LOADS AND FORCES DURING OPERATING CONDITION AS PER APPENDIX 2-3

Hydrostatic end force on area inside of flange [HD]

12 MOMENT ARMS FOR FLANGE LOADS AS PER APPENDIX TABLE 2-6

Radial distance from the bolt circle to intersection of hub and back of flange, as per Appendix 2-3 [R]

Trang 25

13 FLANGE MOMENTS UNDER OPERATING CONDITION AS PER APPENDIX 2-6

Component of moment due to HD [MD]

14 LOADS AND FORCES DURING GASKET SEATING AS PER APPENDIX 2-3

Gasket load for seating condition [HG]

= W

= 307837.2 kgf

15 MOMENT UNDER GASKET SEATING AS PER APPENDIX 2-6

Total moment acting on the flange for gasket seating [MO']

18 FLANGE STRESSES AS PER APPENDIX 2-7 & 2-8

Equivalent moment [Mmax]

Trang 26

= MAX [ MO , MO' x Sfo / Sfa ]

Trang 27

1 DESIGN CONDITIONS ( Design Mode 1 , Corroded Condition )

2 DESIGN CALCULATION AS PER UG-27

Thickness of shell under internal pressure [ti]

= Pi x R / ( S x E - 0.6 x Pi )

= 0.12 x 628 / ( 14.06 x 0.85 - 0.6 x 0.12 )

= 6.343 mm

3 DESIGN CALCULATION OF SHELL THICKNESS UNDER EXTERNAL PRESSURE AS PER UG-28

Allowable external pressure [Pa]

= 4 x B / ( 3 x ( OD / te ) )

= 4 x 2.272 / ( 3 x 284.4 )

= 0.01065 kgf/mm² g

Since Pa > Pe, design is safe

Since available thickness is more than design thickness, design is safe

DESIGN OF SHELL ( INTERNAL AND EXTERNAL PRESSURE ) Main Shell

Design pressure ( internal ) Pi 0.12 kgf/mm² g

Design pressure ( external ) Pe 0.01055 kgf/mm² g

Material of construction SA-516 GR 70 Plt [UNS:K02700]Max allowable stress at design temp S 14.06 kgf/mm²

Nominal thickness required as per TEMA N.A mm

Internal allowance, corrosion + polishing 3 mm

External allowance, corrosion + polishing 0 mm

Trang 28

2 DESIGN CALCULATION AS PER UG 32 d / APPENDIX 1-4 ( c ) :

3 DESIGN CALCULATION AS PER UG 33 d :

Thickness for equivalent external pressure [t]

Since Pa > Pe, design is safe

Since available thickness is more than design thickness, design is safe

DESIGN OF ELLIPSOIDAL HEAD ( INT & EXT PRESSURE ) Dished End (Rear)

Nominal thickness required as per TEMA N.A mm

Internal allowance, corrosion + polishing 3 mm

External allowance, corrosion + polishing 0 mm

Thinning allowance / Under tolerance 1 mm

109

Trang 29

6 LOAD AND MOMENT ( Wind ) :

7 DESIGN OF ANCHOR BOLTS :

Total uplift force on bolts [T]

Available area of bolts [Ab]

= Ar x Nb where, Ar = 217.1 mm², is root area of bolt

Design Mode 1 , Corroded Condition

Trang 30

10 CHECK FOR COMPRESSION PLATE :

Equivalent radial load [f]

Trang 31

6 LOAD AND MOMENT ( Seismic ) :

7 DESIGN OF ANCHOR BOLTS :

Total uplift force on bolts [T]

Available area of bolts [Ab]

= Ar x Nb where, Ar = 217.1 mm², is root area of bolt

Trang 32

10 CHECK FOR COMPRESSION PLATE :

Equivalent radial load [f]

Trang 33

DESIGN CONDITIONS

NOZZLE DATA

SHELL DATA ( Main Shell )

WELD DATA

CALCULATION OF NOZZLE NECK THICKNESS AS PER UG 45

Neck thickness for internal pressure as per UG 45(a)

Formula in Appendix 1-1 , [trn1]

= ( 0.5 x Pi x OD ) / ( Sn x E + 0.4 x Pi )

= ( 0.5 x 0.12 x 168.3 ) / ( 12.02 x 1.0 + 0.4 x 0.12 )

= 0.983 mm

Neck thickness for external pressure as per UG 45(a)

Neck thickness for external pressure as per UG 28

Assumed neck thickness , [trn3] = 0.512 mm

Thickness of shell as per UG 45(b)(1)

Min shell thickness reqd as per UG 27 , [tr1 = trn2]

NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 01

Allowable stress @ design temperature Sn 12.02 kgf/mm²

Internal allowance , corrosion + polishing CAI 3 mm

External allowance , corrosion + polishing CAE 0

Neck thickness (tnp - CAI - CAE) tn 7.973 mm

Max under tolerance on thickness Alw 1.372 mm

Available neck thickness ( tn - Alw ) ta 6.601 mm

Nozzle projection outward ( from vessel outer face ) Lo 150 mm

Total length of nozzle ( Lo + Addn for curvature) L 156 mm

Reinforcement calculation method Isolated Opening

Allowable stress @ design temperature Sv 14.06 kgf/mm²

Min thickness for external pressure tr2 4.466 mm

Trang 34

= MAX { MAX [ trn1, trn3 ] , MIN [ MAX ( trn2 , trn4 ) , 0.875 x t3 ] } for Process Nozzle

= MAX [ trn1, trn3 ] for Access Opening

= 5.387 mm Process OpeningSince available neck thickness, ta >= trn, selected neck thickness is adequate

Trang 35

LOCAL STRESS ANALYSIS (EDGE OF ATTACHMENT) N 01

Design Mode 1, Corroded Condition

Shear stress due to Q , [ t1 ]

Trang 36

7 COMBINING STRESSES :

** Only absolute values of quantities in bracket shall be used while combining stresses

( 1 ) : Fr sign is (+) for outward load, & (-) for inward load

Allowabe Stresses for various catergories:

∑

Membrane 6.593 7.162 5.082 4.514 12.86 12.14 9.728 10.45Mem+Bend 17.24 14.66 -3.601 -1.023 19.74 26.32 5.946 -0.631

Trang 37

LOCAL STRESS ANALYSIS (EDGE OF PAD) N 01

Design Mode 1, Corroded Condition

Trang 38

7 COMBINING STRESSES :

** Only absolute values of quantities in bracket shall be used while combining stresses

( 1 ) : Fr sign is (+) for outward load, & (-) for inward load

Allowabe Stresses for various catergories:

∑

Membrane 7.757 9.869 4.793 2.681 14.49 13.43 8.884 9.947Mem+Bend 12.67 16.99 1.452 -2.87 18.89 29.44 7.051 -3.49

Trang 39

DESIGN CONDITIONS

NOZZLE DATA

SHELL DATA ( Main Shell )

WELD DATA

CALCULATION OF NOZZLE NECK THICKNESS AS PER UG 45

Neck thickness for internal pressure as per UG 45(a)

Formula in Appendix 1-1 , [trn1]

= ( 0.5 x Pi x OD ) / ( Sn x E + 0.4 x Pi )

= ( 0.5 x 0.12 x 168.3 ) / ( 12.02 x 1.0 + 0.4 x 0.12 )

= 0.983 mm

Neck thickness for external pressure as per UG 45(a)

Neck thickness for external pressure as per UG 28

Assumed neck thickness , [trn3] = 0.512 mm

Thickness of shell as per UG 45(b)(1)

Min shell thickness reqd as per UG 27 , [tr1 = trn2]

NOZZLE NECK THICKNESS AND REINFORCEMENT DESIGN N 02

Allowable stress @ design temperature Sn 12.02 kgf/mm²

Internal allowance , corrosion + polishing CAI 3 mm

External allowance , corrosion + polishing CAE 0

Neck thickness (tnp - CAI - CAE) tn 7.973 mm

Max under tolerance on thickness Alw 1.372 mm

Available neck thickness ( tn - Alw ) ta 6.601 mm

Nozzle projection outward ( from vessel outer face ) Lo 150 mm

Total length of nozzle ( Lo + Addn for curvature) L 156 mm

Reinforcement calculation method Isolated Opening

Allowable stress @ design temperature Sv 14.06 kgf/mm²

Min thickness for external pressure tr2 4.466 mm

Trang 40

= MAX { MAX [ trn1, trn3 ] , MIN [ MAX ( trn2 , trn4 ) , 0.875 x t3 ] } for Process Nozzle

= MAX [ trn1, trn3 ] for Access Opening

= 5.387 mm Process OpeningSince available neck thickness, ta >= trn, selected neck thickness is adequate

Định dạng
Số trang	92
Dung lượng	422,71 KB